EP0259106A1 - Ventilantriebsvorrichtung in einer Brennkraftmaschine - Google Patents

Ventilantriebsvorrichtung in einer Brennkraftmaschine Download PDF

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Publication number
EP0259106A1
EP0259106A1 EP87307617A EP87307617A EP0259106A1 EP 0259106 A1 EP0259106 A1 EP 0259106A1 EP 87307617 A EP87307617 A EP 87307617A EP 87307617 A EP87307617 A EP 87307617A EP 0259106 A1 EP0259106 A1 EP 0259106A1
Authority
EP
European Patent Office
Prior art keywords
rocker
rocker arm
fluid supply
passages
rocker arms
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP87307617A
Other languages
English (en)
French (fr)
Other versions
EP0259106B1 (de
Inventor
Tsuneo C/O Kabushiki Kaisha Konno
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP20095586A external-priority patent/JPS6357805A/ja
Priority claimed from JP24267686A external-priority patent/JPS6397808A/ja
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Priority to EP92118069A priority Critical patent/EP0524664B1/de
Publication of EP0259106A1 publication Critical patent/EP0259106A1/de
Application granted granted Critical
Publication of EP0259106B1 publication Critical patent/EP0259106B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2411—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the valve stem and rocker arm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/06—Cutting-out cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/104—Lubrication of valve gear or auxiliaries of tappets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/107—Lubrication of valve gear or auxiliaries of rocker shaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/108—Lubrication of valve gear or auxiliaries of auxiliaries
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F2001/244—Arrangement of valve stems in cylinder heads
    • F02F2001/247—Arrangement of valve stems in cylinder heads the valve stems being orientated in parallel with the cylinder axis
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to valve operating apparatus in an internal combustion engine. More particularly, the invention involves valve operating apparatus of the type including a camshaft rotatably driven by the engine, a plurality of cams on the camshaft for operating the intake or exhaust valves according to a selected mode of operation, and pivotably mounted rocker arms for opening and closing the valves in response to rotation of the cams.
  • driver rocker arms operably connected to the valve or valves to be operated, and free rocker arms, independent of the valves, are disposed adjacent each other and are operable in different modes by rotation of the cams.
  • a selective coupling carried by the rocker arms is hydraulically actuable for selectively interconnecting or disconnecting the respective rocker arms according to the desired mode of valve operation.
  • valve operating devices it is general practice to select relative valve diameters, valve timings, and valve lifts in view of a high-speed range for higher engine output power.
  • an intake valve is actuated at constant valve timing and valve lift throughout a full engine speed range from low to high speeds, then the speed of flow of an air-fuel mixture into the combustion chamber varies from engine speed to engine speed since the amount of air-fuel mixture introduced per unit time varies from engine speed to engine speed.
  • the speed of flow of the air-fuel mixture is lowered, the charging efficiency is lowered, and the air-fuel mixture is not mixed and atomized appropriately in the combustion chamber, resulting in slow combustion therein. Therefore, no stable combustion is achieved, and the engine speed becomes irregular during the low-speed operation. Consequently, the combustion efficiency, the fuel economy, and the knocking margin are all reduced.
  • hydraulic passages for supplying hydraulic pressure respectively to the selective coupling means are defined by dividing the inner space of the rocker shaft by means of a steel ball that is forcibly inserted into and securely positioned in the rocker shaft.
  • selective valve operating means comprising: a plurality of pivotaliy mounted rocker arms, including at least one driver rocker arm having an end operably connecting to a said valve and a free rocker arm selectively connectable with an adjacent driver rocker arm; a plurality of cams mounted for rotation on said engine, each said cam engaging a follower surface on a said rocker arm; hydraulically operated, selectively actuable coupling means carried by respective ones of said rocker arms for selectively inter­connecting or disconnecting adjacent rocker arms; fluid passages in said rocker arms for supplying operating fluid to said coupling means; and means for supplying operating fluid independently to each said fluid passage, including: a rocker shaft having an axial opening mounting said rocker arms for pivotal movement; partition means in said rocker shaft opening defining a plurality of independent fluid supply lines; and means for independently connecting respective ones of said fluid supply lines to respective one of said rocker arm passages.
  • the present invention may provide valve operating means in an internal combustion engine in which valves are controlled in a multitude of speed ranges by a simplified hydraulic pressure supply circuit.
  • the invention contemplates selectively actuable coupling means disposed between adjacent ones of the rocker arms for interconnecting and disconnecting the rocker arms.
  • the valve operating device employs a camshaft having three adjacent cams. Three pivotally mounted rocker arms are held in sliding contact with the respective cams, one of the rocker arms being a free rocker arm and the other two being driver rocker arms operably connected to the intake or exhaust valves for opening and closing them.
  • the selective coupling means between adjacent rocker arms are each independently supplied with operating fluid so that a greater number of engine speed ranges can be controlled.
  • the rocker shaft is divided by axially extending partitions into a plurality of hydraulic pressure supply passages for separate communication with the respective coupling means.
  • the rocker arms By separately and selective actuating the respective coupling means in accordance with the operating conditions of the engine, the rocker arms can be operated in different modes, and the valves can be controlled in a large number of speed ranges.
  • the required hydraulic pressure control circuit is simplified because the hydraulic supply passages defined in the rocker shaft by the axially extending partitions communicate separately with the respective coupling means.
  • the present invention also contemplates, in related embodiments, the independent supply of operating fluid; for example, to hydraulic lash adjusters employed between the rocker arm and the associated valve.
  • fluid such as oil, for lubricating various parts of the apparatus can also be provided.
  • a pair of intake valves la, lb are disposed in the body of an internal combustion engine.
  • the valves la, lb can be opened and closed by a first low-speed cam 3, a second low-­speed cam 4, and a high-speed cam 5 which are integrally formed on a camshaft 2 rotatable in synchronism with rotation of the engine at a speed ratio of l/2 with respect to the speed of rotation of the engine.
  • the cams 3, 4, 5 operate first, second and third rocker arms 7, 8, 9 pivotally supported on a rocker shaft 6 extending parallel to the camshaft 2.
  • the camshaft 2 is rotatably disposed above the engine body.
  • the high-speed cam 5 is integrally formed on the camshaft 2 in alignment with an intermediate position between the intake valves la, lb.
  • the first low-speed cam 3 has a cam profile to meet low-speed operation of the engine and includes a cam lobe 3a projecting radially outwardly to a relatively small extent.
  • the high-speed cam 5 has a cam profile to meet high-speed operation of the engine and includes a cam lobe 5a projecting radially outwardly to a greater extent than the cam lobe 3a, the cam lobe 5a also having a larger angular extent than the cam lobe 3a.
  • the second low-speed cam 4 also has a cam profile to meet the low-­speed operation of the engine and includes a cam lobe 4a projecting radially outwardly to a relatively small extent, the cam lobe 4a being smaller than the cam lobe 3a.
  • the rocker shaft 6 is fixed below the camshaft 2.
  • the first through third rocker arms, 7 through 9, which are operated respectively by the high-speed cam 5, the first low-speed cam 3, and the second low-speed cam 4, are pivotally supported on the rocker shaft 6.
  • the rocker arms 7, 8, 9, have on their upper portions cam slippers 7a, 8a, 9a, held in sliding contact with the cams, 3, 4, 5, respectively.
  • the second and third rocker arms, 8, 9, extend to positions above the intake valves la, lb.
  • Tappet screws l2, l3 are threaded through distal ends of the second and third rocker arms 8, 9 and are engageable with the upper ends of the intake valves la, lb.
  • Flanges l4, l5 are attached to the upper ends of the intake valves la, lb.
  • the intake valves la, lb are normally urged upward, i.e., in a closing direction, by compression coil springs l6, l7 disposed on the intake valves la, lb between the flanges l4, l5 and the engine body.
  • a cylindrical lifter l9 having a closed upper end is disposed as a pushing means in abutment against a lower surface of the end of the first rocker arm 7.
  • the lifter l9 is normally urged upwardly by a lifter spring 20 of relatively weak resiliency interposed between the lifter l9 and the engine body (not shown) for resiliently biasing the cam slipper 7a of the first rocker arm 7 slidably against the high-­speed cam 5.
  • first and second rocker arms 7, 8 are disposed in laterally adjacent sliding contact with each other.
  • a first selectively actuated coupling 2l is operatively disposed between the first and second rocker arms 7, 8 for selectively disconnecting the rocker arms 7, 8 from each other for relative angular displacement and also for interconnecting the rocker arms 7, 8 for their movement in unison.
  • the first and third rocker arms 7, 9 are disposed in laterally adjacent sliding contact with each other.
  • a second selectively actuated coupling 22 is operatively disposed between the first and third rocker arms 7, 9 for selectively disconnecting the rocker arms 7, 9 from each other for relative angular displacement and also for interconnecting the rocker arms 7, 9 for their movement in unison.
  • the first and second selectively actuated couplings 2l, 22 are of an identical construction, and hence only the first coupling 2l will hereinafter be described in detail.
  • the first coupling 2l comprises a piston 23 movable between a position in which it interconnects the first and second rocker arms 7, 8 and a position in which it disconnects the first and second rocker arms 7, 8 from each other. Also provided are a stopper 24 for limiting the movement of the piston 23, and a spring 25 for urging the stopper 24 to move the piston 23 toward the position to disconnect the first and second rocker arms 7 and 8 from each other.
  • the first rocker arm 7 has a first guide hole 26 opening toward the second rocker arm 8 and extending parallel to the rocker shaft 6.
  • the first rocker arm 7 also has a smaller-­diameter hole 28 near the closed end of the first guide hole 26 with a step 27 being defined between the smaller-diameter hole 28 and the first guide hole 26.
  • the piston 23 is slidably fitted in the first guide hole 26. The piston 23 and the closed end of the smaller-diameter hole 28 cooperate to define therebetween a hydraulic pressure chamber 29.
  • the second rocker arm 8 has a second guide hole 35 opening toward the first rocker arm 7 for registration with the first guide hole 26 in the first rocker arm 7.
  • the circular stopper 24 is slidably fitted in the second guide hole 35.
  • the second rocker arm 8 also has a smaller-diameter hole 37 near the closed end of the second guide hole 35 with a step 36 defined between the second guide hole 35 and the smaller-diameter hole 37 for limiting movement of the circular stopper 24.
  • the second rocker arm 8 also has a through-hole 38 defined coaxially with the smaller-diameter hole 37.
  • a guide rod 39 joined integrally and coaxially to the circular stopper 24 extends through the hole 38.
  • a coil spring 25 is disposed around the guide rod 39 between the stopper 24 and the closed end of the smaller-diameter hole 37.
  • the piston 23 has an axial length selected such that, when one end of the piston 23 abuts against the step 27, the other end thereof is positioned at the interface between the first and second rocker arms 7, 8, and, when the piston 23 is moved into the second guide hole 35 until it displaces the stopper 24 into abutment against the step 36, the said one end of the piston 23 remains in the first guide hole 26.
  • the rocker shaft 6 has an axially extending partition 3l forced or fixedly mounted therein or it may be integrally formed therewith.
  • the partition 3l divides the inner space of the rocker shaft 6 into two longitudinally parallel, hydraulic pressure supply passages 32, 33.
  • the first rocker arm 7 has adjacent one end a hydraulic passage 34 defined therein in communication with the hydraulic pressure chamber 29 of the first coupling 2l.
  • the rocker shaft 6 has a hole 40 defined therein and providing communication between the hydraulic passage 34 and the hydraulic passage supply passage 32 irrespective of how the first rocker arm 7 is angularly moved about the rocker shaft 6.
  • the first rocker arm 7 has adjacent to its other end an annular groove 4l surrounding the rocker shaft 6 and a hydraulic passage 42 through which the annular groove 4l communicates with the hydraulic pressure chamber 29 of the second coupling 22.
  • the rocker shaft 6 has a hole 43 providing communication between the hydraulic pressure supply passage 33 and the annular groove 4l.
  • the hydraulic pressure chamber 29 of the first coupling 2l communicates with the hydraulic pressure supply passage 32, and the hydraulic pressure chamber 29 of the second coupling 22 communicates with the hydraulic pressure supply passage 33.
  • the first and second couplings 2l, 22 can thus be operated independently of each other.
  • valve operating mechanism Operation of the valve operating mechanism is as follows.
  • the first and second couplings 2l, 22 are actuated to disconnect the first through third rocker arms 7, 8, 9 from each other as illustrated in Figure 4. More specfically, hydraulic pressure is released from the hydraulic pressure chamber 29, thus allowing the stopper 24 to move toward the first rocker arm 7 under the resiliency of the spring 25 until the piston 23 abuts against the step 27.
  • the second and third rocker arms, 8, 9 are not affected by the angular movement of the first rocker arm 7.
  • the second rocker arm 8 is angularly moved in sliding contact with the first low-speed cam 4, whereas the third rocker arm 9 is angularly moved in sliding contact with the second low-speed cam 5. Therefore, the intake valve la is alternately opened and closed by the second rocker arm 8, and the other intake valve lb is alternately opened and closed by the third rocker arm 9. Any frictional loss of the valve operating mechanism is relatively low because the first rocker arm 7 is held in sliding contact with the high-speed cam 5 under the relatively small resilient force of the lifter spring 20.
  • the intake valve la is alternately opened and closed at the valve timing and valve lift according to the profile of the first low-­speed cam 3, whereas the other intake valve lb is alternately opened and closed at the valve timing and valve lift according to the profile of the second low-speed cam 4. Accordingly, the air-­fuel mixture flows into the combustion chamber at a rate suitable for the low-speed operation of the engine, thereby resulting in stable fuel combustion, improved fuel economy, stable low-speed operation, and prevention of knocking. Since the profiles of the low-speed cams 3, 4 are different, the turbulence of the air-fuel mixture in the combustion chamber is increased for improved fuel economy.
  • the first and second rocker arms 7, 8 are interconnected by the first coupling 2l, with the first and third rocker arms 7, 9 remaining disconnected from each other, as shown in Figure 5. More specifically, the hydraulic pressure chamber 29 of the first coupling 2l is supplied with hydraulic pressure from the hydraulic pressure passage 32 to cause the piston 23 to push the stopper 24 into the second guide hole 35 against the resiliency of the spring 25 until the stopper 24 engages the step 36.
  • the first and second rocker arms 7, 8 are now prevented from relative angular movement, but, instead, are caused to swing in unison.
  • the intake valve la is alternately opened and closed at the valve timing and valve lift according to the profile of the high-speed cam 5, whereas the other intake valve lb is alternately opened and closed at the valve timing and valve lift according to the profile of the second low-speed cam 4.
  • the air-fuel mixture now flows into the combustion chamber at a rate suitable for the medium-speed operation of the engine, resulting in a relatively high charging efficiency and greater turbulence of the air-fuel mixture in the combustion chamber and hence an improved fuel economy, as with the low-speed operation.
  • the first and third rocker arms 7, 9 are interconnected by the second coupling 22, as shown in Figure 6, by supplying hydraulic pressure into the hydraulic pressure chamber 29 of the second coupling 22.
  • the rocker arms 7, 8, 9 are caused to swing by the high-speed cam 5.
  • the intake valves la, lb are alternately opened and closed at the valve timing and valve lift according to the profile of the high-speed cam 5. The charging efficiency is increased to enable the engine to produce high output power and torque.
  • the inner space of the rocker shaft 6 is divided into the hydraulic pressure supply passages 32, 33 by the axially extending partition 3l, and the hydraulic pressure supply passages 32, 33, are held in communication with the hydraulic pressure chambers 29 of the respective first and second couplings 2l, 22. Therefore, the hydraulic pressure can be supplied from one axial end of the rocker shaft 6, thereby making the hydraulic pressure supply circuit simple in a valve operating device in a multicylinder internal combustion engine.
  • the first and third rocker arms 7, 9 may be interconnected, while the first and second rocker arms 7, 8 are disconnected during the medium-speed operation of the engine.
  • the intake valve la is alternately opened and closed at the valve timing and valve lift according to the profile of the first low-speed cam 3
  • the other intake valve lb is alternately opened and closed at the valve timing and valve lift according to the profile of the high-speed cam 5.
  • Figure 7 shows a second embodiment of the present invention.
  • a piston 23 ⁇ is slidably disposed in each of the second and third rocker arms 8, 9, and stoppers 24 ⁇ are slidably disposed in the first rocker arm 7 for urging stoppers 24 toward the pistons 23 ⁇ .
  • the second and third rocker arms 8, 9 have hydraulic passages 34, 42 providing communication between the hydraulic pressure supply passages 32, 33 and the hydraulic pressure chambers 29 of the selective couplings 2l ⁇ , 22 ⁇ .
  • Figure 8 illustrates a third embodiment in which the first coupling 2l is disposed between the first and second rocker arms 7, 8, and the second coupling 22 ⁇ is disposed between the first and third rocker arms 7, 9.
  • the third embodiment is as advantageous as the second embodiment.
  • the first and second low-speed cams 3, 4 of the first embodiment are replaced with circular raised portions 64, 65 integrally formed on the camshaft 2.
  • the arrangement of Figure 9 may be employed in combination with a certain cylinder of a multicylinder internal combustion engine.
  • a low-speed range due to the presence of the circular raised portions 64, 65, both of the intake valves la, lb are kept at rest, thereby disabling the cylinder for highly improved fuel economy.
  • a medium-speed range only one of the intake valves la is operated to increase engine output power.
  • both of the intake valves la, lb are operated for higher engine output power.
  • Figure l0 illustrates a fifth embodiment of the present invention.
  • the second and third rocker arms 8 ⁇ , 9 ⁇ are held against the intake valves la, lb, respectively, through hydraulic tappets Tl, T2.
  • the rocker shaft 6 has therein an axially extending partition 45 of a Y-shaped cross section forced or fixedly mounted therein or integrally formed therewith.
  • the partition 45 divides the inner space of the rocker shaft 6 into three parallel hydraulic pressure supply passages 46, 47, 48.
  • the second and third rocker arms 8 ⁇ , 9 ⁇ have respective hydraulic passages 49 for supplying hydraulic pressure to the respective hydraulic tappets Tl, T2.
  • the rocker shaft 6 has a hole 50 defined therein for providing communication between the hydraulic passages 49 and the hydraulic pressure supply passages 46.
  • a rocker arm (not shown) disposed between the second and third rocker arms 8 ⁇ , 9 ⁇ has annular grooves 5, 52 surrounding the rocker shaft 6 in a position corresponding to the couplings 2l, 22 and also has hydraulic passages 55, 56 through which the hydraulic pressure chambers of the couplings 2l, 22 communicate respectively with the annular grooves 5l, 52.
  • the rocker shaft 6 also has a hole 53 communicating between the hydraulic pressure supply passage 47 and the annular groove 5l and a hole 54 communicating between the hydraulic pressure supply passage 48 and the annular groove 52.
  • each of the hydraulic tappets Tl, T2, the coupling 2l, and the coupling 22 can individually be supplied with hydraulic pressure, and the hydraulic pressure circuit is not complicated.
  • Figure ll shows a sixth embodiment of the present invention.
  • the rocker shaft 6 has an axially extending partition 60 of an X-shaped cross section forced or fixedly mounted therein or integrally formed therewith.
  • the partition 60 divides the inner space of the rocker shaft 6 into four parallel hydraulic pressure supply passages, 46, 47, 48, 59.
  • the hydraulic pressure supply passages 46, 47, 48 communicate with the respective hydraulic pressure chambers of the hydraulic tappets Tl, T2, and with the couplings 2l, 22.
  • the hydraulic pressure supply passage 59 communicates with a hydraulic passage 58 for supplying lubricating oil to the cam slippers and a separate hydraulic passage (not shown) for supplying lubricating oil to the cam journals.
  • a hole 57 defined in the rocker shaft 6 is caused to connect annular grooves 6l defined in the respective rocker arms 7, 8 ⁇ , 9 ⁇ with the hydraulic pressure supply passage 59.
  • the sixth embodiment has an additional advantage in that lubricating oil can be supplied to the slidingly contacting surfaces of the cams 3, 4, 5, to the rocker arms 7, 8 ⁇ , 9 ⁇ and also to the cam journals through a simple hydraulic passage arrangement.
  • a pair of intake valves Vl, V2 are disposed in an engine body l0l, and can be opened and closed by a cam C integrally formed on a camshaft l02 rotatable in synchronism with rotation of the engine at a speed ratio of l/2 with respect to the speed of rotation of the engine, and also by first and second rocker arms l03, l04, angularly movable about an axis parallel to the camshaft l02, and a selectively actuated coupling l05 disposed in the rocker arms l03, l04.
  • the intake valves Vl, V2 are operated selectively in a mode in which both are opened and closed, or a mode in which only intake valve Vl is opened and closed.
  • the engine body l0l also has a pair of exhaust valves (not shown) which can be opened and closed in a manner similar to the intake valves Vl, V2.
  • the camshaft l02 is rotatably disposed above the engine body l0l.
  • the cam C is integrally formed with the camshaft l02 in alignment with the intake valve Vl.
  • the camshaft l02 has an integral concentric surface of the raised portion l06 aligned with the other intake valve V2.
  • the surface of the raised portion l06 is a circle having a radius equal to the radius of the base circle l07 of the cam C.
  • the first rocker arm l03 has an integral cam slipper l08 positioned on its upper surface and held in sliding contact with the cam C
  • the second rocker arm l04 has an integral slipper l09 positioned on its upper surface and held in sliding contact with the raised portion l06.
  • the rocker arms l03, l04 have base portions angularly movably supported on a rocker shaft ll0 fixed to the engine body l0l parallel to the camshaft l02, the base portions being in sliding contact with each other.
  • the rocker arms l03, l04 have on each of their ends housings lll, ll2, respectively, for engaging the upper ends of the respective intake valves Vl, V2.
  • Hydraulic lash adjusters Tl, T2 are disposed in the respective housings lll, ll2.
  • the hydraulic lash adjusters Tl, T2 are basically of the same construction. Accordingly, the structure of only one of the hydraulic lash adjusters, that indicated as T2, will be described in detail.
  • the hydraulic lash adjuster T2 has a hydraulic pressure chamber ll5 defined in the rear side of a plunger ll4 which is normally urged by a spring ll3 to move into engagement with the intake valve V2.
  • a check valve in the form of a ball ll7 is interposed between the hydraulic pressure chamber ll5 and a hydraulic reservoir chamber ll6 communicating with a hydraulic supply source (not shown) at all times.
  • the housing ll2 has a bore ll8 opening toward the intake valve V2.
  • the plunger ll4 which is closed at its lower end, is slidably disposed within the bore ll8.
  • the closed lower end of the plunger ll4 contains a spherical head ll9 directed toward the intake valve V2.
  • a ring l20 is held against the inner surface of the open end of the bore ll8 for preventing the plunger ll4 from being displaced therefrom.
  • the hydraulic reservoir chamber ll6 is defined by a cylindrical member l2l slidably fitted in the plunger ll4.
  • the hydraulic pressure chamber ll5 is defined between the lower end of the cylindrical member l2l and the lower end of the plunger ll4.
  • a valve cage l22 is disposed in the hydraulic pressure chamber ll5 and pressed against the cylindrical member l2l by a spring ll3.
  • the spherical check valve ll7 is floatingly housed in the valve cage l22.
  • the cylindrical member l2l has a valve hole l23 defined in the lower end thereof and communicating with the hydraulic pressure chamber ll5. The communication between the valve hole l23 and the hydraulic pressure chamber ll5 can be closed by the check valve ll7.
  • the cylindrical member l2l has an annular groove l24 provided in its outer surface that communicates via a passage l24 ⁇ with the hydraulic reservoir chamber ll6.
  • the plunger ll4 has an annular groove l25 defined in its outer surface that communicates with the annular groove 24 via passage 25 ⁇ irrespective of relative movement of the cylindrical member 2l and the plunger l4.
  • the cylindrical member 2l is biased upwardly by the force of the spring ll3 to be pressed against the closed end of the bore ll8.
  • the upper end of the cylindrical member l2l has a through-hole l26 communicating with the hydraulic reservoir member chamber l6.
  • the bore ll8, the plunger ll4, and the cylindrical member l2l cooperate at their upper ends to define an annular chamber l27.
  • a vent hole l28 extending through the second rocker arm l04 vents the annular chamber l27 to atmosphere in order to prevent the plunger ll4 from moving due to pressurization and pressure reduction in the annular chamber l27
  • the rocker shaft ll0 has an axially extending partition l36 forced or fixedly mounted therein, or integrally formed therewith.
  • the partition l36 divides the interior of the rocker shaft ll0 into first and second hydraulic pressure supply passages l37, l38.
  • the first and second hydraulic pressure supply passages l37, l38 are individually connected to corresponding hydraulic pressure supply sources (not shown).
  • the first hydraulic pressure supply passage l38 is supplied with a fluid of relatively high hydraulic pressure.
  • the second rocker arm l04 has an annular groove l39 surrounding the rocker shaft ll0.
  • a hole l40 is provided in the rocker shaft ll0 through which the first hydraulic pressure supply passage 37 communicates with the annular groove l39.
  • the second rocker arm l04 has a first hydraulic passage l3l interconnecting the annular groove l39 and the annular groove l25 of the plunger ll4, the first hydraulic passage l3l having a restriction l32.
  • the hydraulic reservoir chamber ll6 of the hydraulic lash adjuster T2 is held in communication with the first hydraulic pressure supply passage l37 at all times.
  • the restriction l32 serves to limit the rate of supply of the hydraulic medium from the first hydraulic pressure supply passage l37.
  • the housing ll2 of the second rocker arm l04 has a restriction l33 in its upper portion communicating with the through-hole l26.
  • This restriction l33 serves to limit the rate of discharge of the hydraulic medium from the hydraulic reservoir chamber ll6.
  • the restrictions l32, l33 therefore, prevent the hydraulic pressure in the hydraulic reservoir chamber ll6 from being abruptly varied.
  • the first rocker arm l03 has an annular groove l4l communicating with the first hydraulic pressure supply passage l37 and a first hydraulic passage l42 connecting the hydraulic lash adjuster Tl and the annular groove l4l.
  • the first hydraulic passage l42 has a restriction (not shown) similar to the restriction l32 in passage l3l.
  • Flanges l34, l35 are mounted on the upper portions of the respective intake valves Vl, V2.
  • the intake valves Vl, V2 are normally urged upwardly in a valve closing direction by valve springs Sl, S2 ( Figure l3) disposed between the flanges l34, l35 and the engine body l0l around the intake valves Vl, V2, respectively.
  • the first and second rocker arms l03, l04 are held in lateral sliding contact with each other.
  • a selectively actuated coupling l05 is arranged in the rocker arms l03, l04 for selectively disconnecting the rocker arms for relative angular displacement and interconnecting them for movement in unison.
  • the coupling l05 includes a piston l5l movable along an axis parallel to the rocker shaft ll0 between a position in which it interconnects the first and second rocker arms l03, l04 and a position in which it disconnects the rocker arms from each other. Also provided are a stopper l52 for limiting the movement of the piston l5l, and a spring l53 for urging the stopper l52 to move the piston l5l toward the position to disconnect the rocker arms from each other.
  • the first rocker arm l03 has a first guide hole l54 opening toward the second rocker arm l04 and extending parallel to the rocker shaft ll0.
  • the first rocker arm l03 also has a smaller-­diameter hole l56 near the closed end of the first guide hole l54, with a step l55 being defined between the smaller-diameter hole l56 and the first guide hole l54.
  • the piston l5l is slidably fitted in the first guide hole l54.
  • the piston l5l and the closed end of the smaller-diameter hole l56 cooperate to define therebetween a hydraulic pressure chamber l57.
  • the first rocker arm l03 also has a second hydraulic passage l58 communicating with the hydraulic pressure supply passage l38 in the rocker shaft ll0 by means of a through-hole l59 defined in the side wall of the rocker shaft ll0.
  • the piston l5l has an axial length such that when its inner end abuts against the step l55, the other end thereof does not project from the side of the first rocker arm l03 facing the second rocker arm l04.
  • the second rocker arm l04 has a second guide hole l60 opening toward the first rocker arm l03 for registration with the first guide hole l54 in the first rocker arm l03, the second guide hole l60 having the same diameter as that of the first guide hole l54.
  • the circular stopper l52 is slidably fitted in the second guide hole l60.
  • the second rocker arm l04 also has a smaller-diameter hole l62 near the closed end of the second guide hole l60, with a step l6l defined between the second guide hole l60 and the smaller-diameter hole l62 for limiting movement of the circular stopper l52.
  • the second rocker arm l04 also has a through-hole l63 defined coaxially with the smaller-diameter hole l62 and smaller in diameter than the hole l62, the hole l63 extending between the bottom of the hole l62 and the outer side of the second rocker arm l04.
  • a guide rod l64 joined integrally and coaxially to the circular stopper l52, extends through the hole l63.
  • the coil spring l53 is disposed around the guide rod l64 between the stopper l52 and the closed end of the smaller-­diameter hole l62.
  • the first and second guide holes l54, l60 are aligned coaxially with each other when the cam slipper l08 of the first rocker arm l03 slidingly contacts the base circle l07 of the cam C and the slipper of the second rocker arm l04 slidingly contacts the circular raised portion l06.
  • the hydraulic lash adjusters Tl, T2 are supplied with a relatively low hydraulic pressure, and the coupling l05 is supplied with a relatively high hydraulic pressure.
  • the hydraulic lash adjusters Tl, T2 and the coupling l05 can, therefore, each be operated under suitable hydraulic pressures that can differ from one another.
  • Figure l5 shows another embodiment of the present invention.
  • the coupling l05 is disposed across a first hydraulic passage l42 ⁇ by which the hydraulic lash adjuster Tl of the first rocker arm l03 and the first hydraulic pressure supply passage l37 are connected.
  • the first rocker arm l03 has an annular groove l65 which surrounds the piston l5l of the coupling l05 at all times.
  • the first hydraulic passage l42 ⁇ communicates with the annular groove l65 thereby establishing fluid communication between the passage l42 ⁇ and the hydraulic supply passage l37 via the hole l40 ⁇ in the rocker shaft ll0 and the groove l5l in the rocker arm l03.
  • Figure l6 illustrates yet another embodiment of the present invention.
  • first and second rocker arms l03, l04 are angularly movably supported at their intermediate portions on the rocker shaft ll0.
  • Hydraulic lash adjusters Tl, T2 engaging the intake valves Vl, V2, respectively, are disposed in ends of the respective rocker arms l03, l04.
  • a cam slipper l08 is defined on the lower portion of the opposite end of the first rocker arm l03 and held in sliding contact with the cam C
  • a slipper 9 is similarly defined on the lower portion of the opposite end of the second rocker arm l04 and held in sliding contact with the circular raised portion l06.
  • the selectively actuated coupling l05 is disposed in the rocker arms l03, l04 in a position displaced from the rocker shaft ll0 toward the opposite ends of the rocker arms.
  • the rocker shaft ll0 has its second hydraulic pressure supply passage l38 connecting with the coupling l05 and its first hydraulic pressure supply passage l37 connecting with the hydraulic lash adjusters, Tl, Tl, the first and second hydraulic pressure supply passages, 37, 38, being defined on opposite sides of the partition l36.
  • the second hydraulic pressure passage l38 and the coupling l05 are interconnected by a second hydraulic passage l58, and the hydraulic lash adjusters Tl, T2, and the first hydraulic passages l42, l3l.
  • the coupling l05 is disposed in the first and second rocker arms l03, l04 in a position displaced from the rocker shaft ll0 toward the hydraulic lash adjusters Tl, T2.
  • Annular grooves l4l, l39 communicating with the first hydraulic pressure supply passage l37 are defined in the first and second rocker arms, l03, l04, respectively, in surrounding relation to the rocker shaft ll0.
  • the hydraulic lash adjusters Tl, T2, and the annular grooves l4l, l39, are connected by the individual first hydraulic passages l42, l3l.
  • the coupling l05 is fluidly connected to the second hydraulic pressure supply passage l38 via the second hydraulic passage l58.
  • a hydraulic lash adjuster T is mounted on the rocker arm l03.
  • the rocker arm l03 which is swingably driven by the cam C, is engaged by a single intake valve V.
  • the selectively actuated coupling l05 is disposed between the rocker arm l03 and a separate rocker arm l04 that is held in sliding contact with the circular raised portion l06 on the camshaft 2.
  • the rocker arm l03 has a first hydraulic passage (not shown) leading to the hydraulic lash adjuster T and a second hydraulic passage (not shown) leading to the selective coupling l05.
  • one of a pair of rocker arms l03, l04, between which a selectively actuated coupling l05 is disposed e.g., the rocker arm l04
  • the rocker arm l04 has a first hydraulic passage l3l defined therein across the coupling l05, and the arms l04a, l04b have respective second hydraulic passages l3la, l3lb, connecting the first hydraulic passage l3l and the respective hydraulic lash adjusters.
  • the other rocker arm l03 has a hydraulic passage l58 leading to the coupling l05.
  • hydraulic lash adjusters (not shown) engaging respective intake valves are mounted respectively on rocker arms l7l, l72, that are swingable in sliding contact with respective cams (not shown).
  • a rocker arm l73 is disposed between the rocker arms l7l, l72 and held in sliding contact with a circular raise portion, similar to the previously described raised portions l06 on the camshaft.
  • Selectively actuated couplings l05 ⁇ are disposed between the rocker arms l7l, l73 and between the rocker arms l72, l73, respectively.
  • the rocker arms l7l, l72 have first hydraulic passages l74, l75, respectively, interconnecting the hydraulic lash adjusters and a first hydraulic pressure supply passage l37.
  • the rocker arms l73 has a pair of second hydraulic passages l76 by means of which the couplings l05 ⁇ are connected to the second hydraulic pressure supply passage l38.
  • the rocker arm l7l has a first hydraulic passage l74; the rocker arm l72 has first and second hydraulic passages l75, l76; and rocker arm l73 has a second hydraulic passage l77.
  • first and second hydraulic passages can be provided for any number of valves and any particular arrangement of rocker arms and selectively actuated couplings, which may vary from control mode to control mode.
  • Two second hydraulic passages can independently be provided in order to allow three-mode control.
  • the hydraulic pressure supply system even one used in a multicylinder internal combustion engine, can be simplified. Additionally, the number of separate hydraulic pressure passages can be selected so as to additionally provide operating fluid to hydraulic lash adjusters and oil to lubricate the operating parts of the apparatus.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
EP87307617A 1986-08-27 1987-08-27 Ventilantriebsvorrichtung in einer Brennkraftmaschine Expired - Lifetime EP0259106B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP92118069A EP0524664B1 (de) 1986-08-27 1987-08-27 Ventilantriebsvorrichtung in einer Brennkraftmaschine

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP200955/86 1986-08-27
JP20095586A JPS6357805A (ja) 1986-08-27 1986-08-27 内燃機関の動弁装置
JP242676/86 1986-10-13
JP24267686A JPS6397808A (ja) 1986-10-13 1986-10-13 内燃機関の動弁装置

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EP92118069.1 Division-Into 1987-08-27
EP92118069A Division-Into EP0524664B1 (de) 1986-08-27 1987-08-27 Ventilantriebsvorrichtung in einer Brennkraftmaschine

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EP0259106A1 true EP0259106A1 (de) 1988-03-09
EP0259106B1 EP0259106B1 (de) 1993-05-26

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EP92118069A Expired - Lifetime EP0524664B1 (de) 1986-08-27 1987-08-27 Ventilantriebsvorrichtung in einer Brennkraftmaschine
EP87307617A Expired - Lifetime EP0259106B1 (de) 1986-08-27 1987-08-27 Ventilantriebsvorrichtung in einer Brennkraftmaschine

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US (1) US4777914A (de)
EP (2) EP0524664B1 (de)
CA (1) CA1308977C (de)
DE (2) DE3751935T2 (de)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0291357A1 (de) * 1987-05-15 1988-11-17 Honda Giken Kogyo Kabushiki Kaisha Ventilsteuervorrichtung für Brennkraftmaschine
GB2196694B (en) * 1986-10-23 1990-09-26 Honda Motor Co Ltd Variable valve operation device in internal combustion engine
FR2653164A1 (fr) * 1989-10-12 1991-04-19 Nissan Motor Agencement de culbuteur pour train de soupapes d'un moteur a combustion interne du type a reglage variable des soupapes.
EP0267687B1 (de) * 1986-10-16 1992-01-02 Mazda Motor Corporation Ventilantriebsvorrichtung für eine Brennkraftmaschine
US5287830A (en) * 1990-02-16 1994-02-22 Group Lotus Valve control means
WO1994021899A1 (en) * 1993-03-25 1994-09-29 Lotus Cars Limited Valve control means
US5351662A (en) * 1990-02-16 1994-10-04 Group Lotus Plc Valve control means
WO1995000750A1 (de) * 1993-06-18 1995-01-05 Ina Wälzlager Schaeffler Kg Schlepphebel für die betätigung von gaswechselventilen
US5386806A (en) * 1990-02-16 1995-02-07 Group Lotus Limited Cam mechanisms
WO1995004873A1 (de) * 1993-08-05 1995-02-16 Bayerische Motoren Werke Aktiengesellschaft Schwinghebel-baugruppe mit miteinander verbindbaren armen
EP0639694A1 (de) * 1993-08-19 1995-02-22 Honda Giken Kogyo Kabushiki Kaisha Ventiltriebvorrichtung für Brennkraftmaschine
FR2710104A1 (fr) * 1993-09-16 1995-03-24 Daimler Benz Ag Procédé de fabrication d'un arbre de culbuteurs pour moteurs à combustion interne.
WO1995010694A1 (de) * 1993-10-14 1995-04-20 Audi Ag Ventiltrieb für eine mehrzylinder-brennkraftmaschine
EP0704619A1 (de) 1994-09-29 1996-04-03 Mercedes-Benz Ag Kraftstoffeinspritzanlage für eine mehrzylindrige Brennkraftmaschine
US5694894A (en) * 1993-03-25 1997-12-09 Lotus Cars Limited Valve control means
WO2003023197A1 (de) 2001-09-11 2003-03-20 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ventiltrieb für eine brennkraftmaschine
WO2006119882A1 (de) * 2005-05-06 2006-11-16 Daimlerchrysler Ag Gaswechselventilbetätigungsvorrichtung
EP1914397A2 (de) * 2006-10-10 2008-04-23 Delphi Technologies, Inc. Hydraulische Schaltung für schaltbare Schlepphebel
WO2009083062A1 (de) * 2007-12-21 2009-07-09 Daimler Ag Zylinderkopfeinheit
EP2400122A1 (de) * 2007-08-23 2011-12-28 Honda Motor Co., Ltd. Ventilbetriebssteuerungssystem für einen Verbrennungsmotor

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS643208A (en) * 1987-06-23 1989-01-09 Honda Motor Co Ltd Tappet valve system for internal combustion engine
US4942854A (en) * 1988-03-03 1990-07-24 Honda Giken Kogyo Kabushiki Kaisha Valve operating device for use in internal combustion engine
DE4308535A1 (de) * 1992-03-30 1993-10-07 Volkswagen Ag Brennkraftmaschine mit einem desaktivierbaren Ladungswechselventil
DE4327943A1 (de) * 1993-08-19 1995-02-23 Audi Ag Ventilsteuerung für eine Brennkraftmaschine
DE4408808A1 (de) * 1994-03-16 1995-09-21 Iav Motor Gmbh Ventiltrieb mit einem unwirksamschaltbaren oder zwei alternativ wirksamschaltbaren Nocken für Ladungswechselventile von Brennkraftmaschinen
DE4410288C1 (de) * 1994-03-24 1995-06-14 Audi Ag Ventilbetätigungsvorrichtung für eine Brennkraftmaschine
US5544626A (en) * 1995-03-09 1996-08-13 Ford Motor Company Finger follower rocker arm with engine valve deactivator
US5613469A (en) * 1995-12-26 1997-03-25 Chrysler Corporation Controls apparatus for engine variable valve system
US5590627A (en) * 1996-01-02 1997-01-07 Chrysler Corporation Fluid inletting and support structure for a variable valve assembly
DE19610107A1 (de) * 1996-03-15 1997-09-18 Schaeffler Waelzlager Kg Kipp- oder Schlepphebel mit einem Ventilspielausgleichselement
JP2002227667A (ja) * 2001-01-30 2002-08-14 Yamaha Motor Co Ltd 内燃機関の可変動弁装置
US6886533B2 (en) * 2003-01-03 2005-05-03 Ford Global Technologies, Llc Internal combustion engine with multiple intake valves and variable valve actuation and timing
KR100921045B1 (ko) * 2006-10-10 2009-10-08 현대자동차주식회사 차량용 실린더 정지장치 및 이를 이용한 가변밸브리프트장치
DE102008016976A1 (de) 2007-04-27 2008-10-30 Schaeffler Kg Achse zur Lagerung von Ventilbetätigungshebeln und Verfahren zur Herstellung der Achse
US7845324B2 (en) * 2008-01-16 2010-12-07 Gm Global Technology Operations, Inc. Sliding-pivot locking mechanism for an overhead cam with multiple rocker arms
US8813698B2 (en) 2009-03-06 2014-08-26 Toyota Jidosha Kabushiki Kaisha Variable valve apparatus of internal combustion engine
CN102588137B (zh) * 2012-03-28 2014-03-12 东风朝阳朝柴动力有限公司 脉冲供油式发动机气缸体油道
JP6090230B2 (ja) * 2014-05-14 2017-03-08 トヨタ自動車株式会社 内燃機関の制御装置及び内燃機関の可変動弁装置
CN106948897A (zh) * 2017-02-20 2017-07-14 浙江大学 一种可变气门数的发动机配气机构
DE102017113783A1 (de) * 2017-06-21 2018-12-27 Man Truck & Bus Ag Kraftübertragungsvorrichtung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2159877A (en) * 1984-05-01 1985-12-11 Honda Motor Co Ltd Actuating valves of i c engine
EP0213758A1 (de) * 1985-07-31 1987-03-11 Honda Giken Kogyo Kabushiki Kaisha Ventilantriebsmechanismus

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU551310B2 (en) * 1983-06-06 1986-04-24 Honda Giken Kogyo Kabushiki Kaisha Valve actuating mechanism
JPS608407A (ja) * 1983-06-29 1985-01-17 Honda Motor Co Ltd 内燃機関の弁作動制御装置
JPS6027717A (ja) * 1983-07-27 1985-02-12 Honda Motor Co Ltd 給油装置
US4523550A (en) * 1983-09-22 1985-06-18 Honda Giken Kogyo Kabushiki Kaisha Valve disabling device for internal combustion engines
US4556025A (en) * 1983-11-18 1985-12-03 Mazda Motor Corporation Engine valve mechanism having valve disabling device
JPS611812A (ja) * 1984-06-12 1986-01-07 Nissan Motor Co Ltd 内燃機関の動弁装置
DE3523531A1 (de) * 1984-07-02 1986-02-13 Honda Giken Kogyo K.K., Tokio/Tokyo Ventilbetaetigungseinrichtung mit sperrfunktion fuer einen verbrennungsmotor
JPS6119911A (ja) * 1984-07-06 1986-01-28 Honda Motor Co Ltd 内燃機関の動弁装置
JPS6131610A (ja) * 1984-07-24 1986-02-14 Honda Motor Co Ltd 内燃機関の弁作動休止装置
JPS6131613A (ja) * 1984-07-24 1986-02-14 Honda Motor Co Ltd 内燃機関の弁作動休止装置
JPH0239607B2 (ja) * 1984-09-04 1990-09-06 Honda Motor Co Ltd Nainenkikannodobensochi
US4627391A (en) * 1984-12-24 1986-12-09 General Motors Corporation Engine valve train system
US4726332A (en) * 1985-04-26 1988-02-23 Mazda Motor Corporation Variable valve mechanism for internal combustion engines
DE3613912A1 (de) * 1985-04-26 1986-10-30 Mazda Motor Corp., Hiroshima Variabler ventilmechanismus fuer verbrennungsmotoren

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2159877A (en) * 1984-05-01 1985-12-11 Honda Motor Co Ltd Actuating valves of i c engine
EP0213758A1 (de) * 1985-07-31 1987-03-11 Honda Giken Kogyo Kabushiki Kaisha Ventilantriebsmechanismus

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, vol. 10, no. 167 (M-488)[2223], 13th June 1986; & JP-A-61 19 911 (HONDA GIKEN KOGYO K.K.) 28-01-1986 *
PATENT ABSTRACTS OF JAPAN, vol. 10, no. 253 (M-512)[2309], 29th August 1986; & JP-A-61 81 510 (HONDA MOTOR CO. LTD) 25-04-1986 *

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0267687B1 (de) * 1986-10-16 1992-01-02 Mazda Motor Corporation Ventilantriebsvorrichtung für eine Brennkraftmaschine
GB2196694B (en) * 1986-10-23 1990-09-26 Honda Motor Co Ltd Variable valve operation device in internal combustion engine
EP0291357A1 (de) * 1987-05-15 1988-11-17 Honda Giken Kogyo Kabushiki Kaisha Ventilsteuervorrichtung für Brennkraftmaschine
FR2653164A1 (fr) * 1989-10-12 1991-04-19 Nissan Motor Agencement de culbuteur pour train de soupapes d'un moteur a combustion interne du type a reglage variable des soupapes.
US5351662A (en) * 1990-02-16 1994-10-04 Group Lotus Plc Valve control means
US5287830A (en) * 1990-02-16 1994-02-22 Group Lotus Valve control means
US5386806A (en) * 1990-02-16 1995-02-07 Group Lotus Limited Cam mechanisms
US5419290A (en) * 1990-02-16 1995-05-30 Group Lotus Limited Cam mechanisms
WO1994021899A1 (en) * 1993-03-25 1994-09-29 Lotus Cars Limited Valve control means
US5694894A (en) * 1993-03-25 1997-12-09 Lotus Cars Limited Valve control means
WO1995000750A1 (de) * 1993-06-18 1995-01-05 Ina Wälzlager Schaeffler Kg Schlepphebel für die betätigung von gaswechselventilen
US5622146A (en) * 1993-06-18 1997-04-22 Ina Walzlager Schaeffler Kg Finger lever for actuating gas exchange valves
WO1995004873A1 (de) * 1993-08-05 1995-02-16 Bayerische Motoren Werke Aktiengesellschaft Schwinghebel-baugruppe mit miteinander verbindbaren armen
US5680835A (en) * 1993-08-05 1997-10-28 Bayerische Motoren Werke Aktiengesellschaft Rocker assembly with interconnectable arms
EP0639694A1 (de) * 1993-08-19 1995-02-22 Honda Giken Kogyo Kabushiki Kaisha Ventiltriebvorrichtung für Brennkraftmaschine
US5495832A (en) * 1993-08-19 1996-03-05 Honda Giken Kogyo Kabushiki Kaisha Valve operating device for internal combustion engine
US5476075A (en) * 1993-09-16 1995-12-19 Mercedes-Benz Ag Hollow rocker-arm shaft for internal combustion engines
FR2710104A1 (fr) * 1993-09-16 1995-03-24 Daimler Benz Ag Procédé de fabrication d'un arbre de culbuteurs pour moteurs à combustion interne.
US5832891A (en) * 1993-10-14 1998-11-10 Audi A.G. Valve gear mechanism for a multi-cylinder internal combustion engine
WO1995010694A1 (de) * 1993-10-14 1995-04-20 Audi Ag Ventiltrieb für eine mehrzylinder-brennkraftmaschine
EP0704619A1 (de) 1994-09-29 1996-04-03 Mercedes-Benz Ag Kraftstoffeinspritzanlage für eine mehrzylindrige Brennkraftmaschine
US5553592A (en) * 1994-09-29 1996-09-10 Mercedes-Benz Ag Fuel injection arrangement for a multicylinder internal combustion engine
DE4434783C2 (de) * 1994-09-29 1998-04-09 Daimler Benz Ag Kraftstoffeinspritzanlage für eine mehrzylindrige Brennkraftmaschine
DE4434783A1 (de) * 1994-09-29 1996-04-11 Daimler Benz Ag Kraftstoffeinspritzanlage für eine mehrzylindrige Brennkraftmaschine
WO2003023197A1 (de) 2001-09-11 2003-03-20 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ventiltrieb für eine brennkraftmaschine
WO2006119882A1 (de) * 2005-05-06 2006-11-16 Daimlerchrysler Ag Gaswechselventilbetätigungsvorrichtung
US7827951B2 (en) 2005-05-06 2010-11-09 Daimler Ag Gas exchange valve actuating apparatus
EP1914397A2 (de) * 2006-10-10 2008-04-23 Delphi Technologies, Inc. Hydraulische Schaltung für schaltbare Schlepphebel
EP1914397A3 (de) * 2006-10-10 2008-07-09 Delphi Technologies, Inc. Hydraulische Schaltung für schaltbare Schlepphebel
US7455040B2 (en) 2006-10-10 2008-11-25 Delphi Technologies, Inc. Hydraulic circuit for switchable cam followers
EP2400122A1 (de) * 2007-08-23 2011-12-28 Honda Motor Co., Ltd. Ventilbetriebssteuerungssystem für einen Verbrennungsmotor
US8220425B2 (en) 2007-08-23 2012-07-17 Honda Motor Co., Ltd. Valve operation control system for internal combustion engine
WO2009083062A1 (de) * 2007-12-21 2009-07-09 Daimler Ag Zylinderkopfeinheit

Also Published As

Publication number Publication date
DE3751935T2 (de) 1997-02-20
CA1308977C (en) 1992-10-20
US4777914A (en) 1988-10-18
EP0524664A2 (de) 1993-01-27
DE3785983D1 (de) 1993-07-01
EP0524664A3 (en) 1993-04-07
EP0259106B1 (de) 1993-05-26
DE3751935D1 (de) 1996-11-28
EP0524664B1 (de) 1996-10-23
DE3785983T2 (de) 1993-12-16

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